Counterbalancing control for a laundry machine



Feb. 28, 1967 A. u. KHAN 3,306,453

COUNTERBALANCING CONTROL FOR A LAUNDRY MACHINE Filed May 12, 1964 3 Sheets-Sheet l INVENTOR.

BY al; AT7 \NEYS A. u. KHAN 3,306,453 COUNTERBALANCING CONTROL FOR A LAUNDRY MACHINE Feb. 28, 1967 3 Sheets-Sheet 2 Filed May 12, 1964 INVENTORQ flmczfl a zyfiafl A T )RNISYS Feb. 28, 1967 A. u. KHAN 3,306,453

' COUNTERBALANCING CONTROL FOR A LAUNDRY MACHINE Filed May 12, 1964 3 Sheets-Sheet 5 J T()RNEYS United States Patent poration of Delaware Filed May 12, 1964, Ser. No. 366,856 9 Claims. (Cl. 210-444) The present invention relates generally to means for counterbalancing unsymmetrically distributed centrifugal forces in a rotating body, and more particularly concerns automatic counterbalancing control means especially adapted for laundry apparatus wherein a horizontal or substantially horizontal axis type drum containing a batch of materials being laundered may be rotated at high speeds for optimum Water extraction, without the detrimental effects caused by excessive uncontrolled vibrations.

By way of example, an empty laundry receiving cylinder or drum rotated about its bearing axis parallels an optimum operating condition, but when a load is introduced into the cylinder, the load is likely to be distributed in such a manner that the center of mass of the loaded cylinder will not coincide with the cylinder bearing axis, but will be eccentrically disposed, thereby producing an unbalanced centrifugal force which is directly proportional to the weight of the unbalanced portion of the total rotating mass and the square of the velocity of such unbalanced weight and inversely proportional to the radius of the unbalanced weight from the axis of rotation of the cylinder.

In addition to affecting the power input necessary to rotate the cylinder or drum, an unbalanced condition causes serious vibration conditions which are even more pronounced in horizontal machines than in vertical axis machines since the unbalanced force directly substantially opposite the gravitational force acting on the machine may be sufficiently great actually to lift the machine from its supporting surface and produce a violent movement, sometimes referred to as walking.

Considerable attention has been given to this problem in the prior art but with only meager success, imposing undesirable complexities into the apparatus, often requiring elaborate electrical or other gadgetry, increased cabinet size, and the like.

It is, accordingly, an important object of the present invention to provide a new and improved means for automatically controlling the counterbalacing of centrifuging apparatus in a simple, efiicient, direct and substantially foolproof manner.

Another object of the invention is to provide automatic counterbalancing means which is entirely mechanical in the control arrangement.

A further object of the invention is to provide a new and improved means for counterbalancing centrifuging apparatus by the automatic distribution of liquid into counterbalancing pockets about the periphery of the centrifuge rotor.

A still further object of the invention is to provide a novel control valve arrangement for automatic control means operative to correct imbalances during high speed centrifuge operation.

Yet another object of this invention is to provide a new and improved centrifuge balancing system having a novel mechanical form of imbalance eccentricity pickup device and amplifying means for controlling counterbalancing means.

A yet further object of the invention is to providecounterbalancing means for a rotating receptacle wherein balancing liquid is selectively controlled and distributed for balancing purposes in a novel manner.

It is also an object of this invention to provide an improved sensing mechanism and translating means for a counterbalancing system.

An additional object of the invention is to provide a new and improved indexing mechanism for loading the correct amount of counterbalancing liquid into vibrationally responsively selective counterbalancing chambers of a centrifuge and which mechanism is free from impact parts which would offer any service problems.

Other objects, features and advantages of the present invention will be readily apparent from the following detailed description of certain preferred exemplary embodiments thereof taken in conjunction with the accompanying drawings in which:

FIGURE 1 is a generally schematic rear elevational view of a centrifuge apparatus as exemplified in a clothes washing machine;

FIGURE 2 is a vertical sectional fragmental detail view taken substantially on the line II-II but with certain parts realigned in the figure merely for illustrative purposes;

FIGURE 3 is a fragmentary rear elevational view taken substantially in the plane of line IIIIII of FIGURE 2;

FIGURE 4 is a similar view but showing a modification;

FIGURE 5 is a side elevational view of the structure of FIGURE 4;

FIGURE 6 is an enlarged fragmentary sectional detailview taken substantially on the line VIVI of FIGURE 2;

FIGURE 7 is an enlarged fragmentary sectional elevational view through the valve structure encircled at VII 7 in FIGURE 1;

FIGURES 8 and 9 are diagrammatic views of the rotating cylinder showing the relative position of the crank pin includes an outer cabinet 11 mounted on a base 12 and 9 having the customary provisions of a front wall access door (not shown) through which a batch of materials to be laundered may be placed in or withdrawn from a treatment zone within the machine and including a tank 13 to which wash water is introduced through a mixing valve 14 and within which a perforate drum 15 is rotatably mounted on a horizontal axis.

Rotary support for the drum 15 is provided by a corotative hollow tubular shaft 17 (FIG. 2) which is journaled in a suitable bearing structure 18 carried by a supporting frame mounted on the base 12 and comprising a pylon structure 19 (FIG. 1) including a horizontal supporting cross bar 20 carried at its opposite ends by upright leg bars 21 which are spaced inwardly from the adjacent walls of the cabinet 11. Driving of the drum 15 rotatably is effected through a pulley 22 fixedly mounted corotatively on the rear end of the shaft 17 as by means of a sleeve nut 23 clamping the hub of the pulley to the end of the shaft as shown in FIGURE 2. A drive belt 24 is trained over the pulley 22 and over a drive pulley 25 on the drive shaft of an electric-a1 motor driven power drive transmission 27 (FIG. I). Cyclical operation of the machine including the mixing valve 14 and the power source for the power drive 27 is accomplished in any suitable or preferred manner as is well known through electrical circuitry, timing means and the like for operating the machine through a program which includes washing, risnsing, extracting and drying periods or phases of operation.

Especially in the spin drying portion of the machine cycle eccentric load displacement causes vibratory movements of the drum and associated mechanism eccentrically to the rotary axis, and such eccentric displacements due to the unbalanced loading conditions cause corresponding oscillatory movements of the pylon frame 19. According to the present invention, such unbalanced load induced vibrations or oscillatory movements of the pylon 19 are sensed and amplified mechanically and trans= lated to control a counterbalancing system. To this end, sensing means are provided comprising an oifbalance motion indicator lever arm 28 conveniently of generally V-shape having the remote ends of its arms rigidly secured to the cross bar 20 of the pylon and with its apex a substantial distance below the cross arm and adjacent to the rigid base 12, as best seen in FIGURE 1.

Connected to the lower apical portion of the arm 28 is an offbalance motion magnifying device comprising (FIGS. 1 and 2) a motion multiplying lever 29 connected adjacent to but spaced from one of it ends on a pivot 30 to a mounting bracket 31 suitably secured rigidly to the base 12 and supporting the lever 29 with its short end portion adjacent to the apical end of the lever arm 28 to which such short end of the lever 29 is secured operatively by means of a link 32. Through this arrangement, oscillatory movements of the arm 28 effect corresponding oscillations of the motion magnifier lever 29, the end of the longer portion of which swings through an amplified length of arc, such as in a four-to-one ratio. Such longer oscillations of the longer portion of the magnifying lever 29 are transmitted into longitudinal corresponding reciprocations of a flexible transmission member, herein comprising a Bowden wire 33 extending through a guide tube 34 having its remote terminal end portion secured by means such as a bracket 35 to a supporting bracket plate or frame 37 mounted on the rear side of the pylon bar 20 in rearward clearance relation to the pulley 22.

Amplified oscillations of the pylon 19 transmitted through the wire 33 control a yoke 38 secured to the end of the transmission wire which extends beyond the bracket 35. Normally, in the absence of load-induced eccentric vibrations of the rotary receptable 15, the relationship is such that the yoke 38 serves as restraining means acting through a crank pin 39 projecting rearwardly from a control valve shaft 40 having rigidly on its front end a proportional control valve 41 conveniently constructed as an integral disk flange on the shaft, as best seen in FIGURES 2 and 6. Adjacent to its rear end, the valve shaft 40 is journaled in a suitable bearing aperture in the base of a generally cup-shaped forwardly opening water intake housing member 42 rigidly supported by the mounting frame plate 37. Front end bearing support for the shaft 40 is provided by a rearwardly projecting smaller diameter bearing stud 43 extending into an axial blind end bearing bore 44 in the front end of the shaft. This bearing stud 43 is mounted on or comprises an integral projection from a partition 45 within a distributor housing member 47 rigidly secured coaxially to the rear end of the rotor shaft 17, as through the nut member 23 and having its rear end portion in relatively telescoped relation to the front end portion of the water intake housing member 42 and suitably sealed for relative rotation while confining liquid within a distributor chamber 48 defined within the water intake housing member 42 and the por-' tion of the rotor shaft carried distributor housing member 47 forwardly from the end of the housing 42 and within which the proportional control valve 41 is accommodated. Through this arrangement, the housing assembly provides a manifold about the valve shaft 40 from which liquid supplied through a conduit 49 ported into the water intake housing member 42 is controlled by the proportional control valve 41 for delivery through distributor orifices 50 through the partition 45, the rear face of which provides a sliding seat against which the front face of the proportional control valve 41 engages for distributor orifice control.

While there may be as many of the distributor orifices 50 as desired or required, in the exemplary arrangement disclosed, especially suitable for a domestic size washing machine, three of the orifices equidistantly spaced both radially and circumferentially about the rotary axis of the shaft 18 have been provided, and the perimeter of the proportional control valve 41 is contoured to afford, as best seen in FIG. 6, a generally segmental shape or lobar form wherein the maximum radius is described preferably on the diameter of a circle sufficient to overlap and completely shut off at least one of the orifices 50, but preferably being of large enough area to enable simultaneous closing off of two of the orifices 50, as indicated in dash outline in FIGURE 6. On the remainder of its perimeter, the valve 41 presents a substantially receded edge 51 which, for smooth flow control and cut off purposes is preferably of arcuate form. Thus, upon relative rotation of the partition 45 and the valve 41, the valve acts as a shutter in respect to the orifices 50, at all times leaving at least one of the orifices exposed to the water intake manifold chamber 48 but also capable of substantially exposing two of the orifices to the water intake manifold chamber, or exposing one of the orifices fully and another of the orifices partially to an infinitely variable degree depending on the location of the off balance load in the perforated drum 15. At the same time, at least one of the orifices 50 of the set of orifices is always shut off.

Leading forwardly from each of the orifices 50 is a nipple 52 projecting forwardly from the partition 45 and to each of which is attached a respective conduit 53 which may conveniently comprise a suitable flexible tube. Each of the conduits 53 is connected at its opposite end to deliver liquid received through its distributor orifice into a pocket, balancing recess receptacle or compartment 54 located on or adjacent to the periphery of the rotor 15 (FIG. 1). These balancing compartments 54 are suitably constructed and arranged equidistantly about the circumference of the rotor or drum 15 and will centrifugally retain liquid supplied thereto but will permit the liquid to drain therefrom when the drum is moving at a decelerated or decelerating speed so as to be self-emptying after their counterbalancing function has been concluded, as when the machine has been shut off by the manual or automatic machine circuit control means at the end of an operating cycle or for any other reason.

During normal, substantially balanced operating rotation of the drum 15, free from any undesirable load eccentricities or unbalancing distribution, or at least without undesirable vibratory or oscillatory movements of the supporting pylon 19, the balancing system merely idles, with the flexible transmission element 33 holding the yoke 38 to restrain the crank pin 39 and thus the proportional control valve disk shaft 40 against rotation. At the same time, the liquid supply conduit 49 remains inactive by being shut off from source and no balancing liquid is thus delivered to the manifold chamber 48. As shown in FIGURE 3, the normal, vibration-free position of the yoke 38 restrains the crank pin 39 at about from an axis through the center of the shaft 40 and aligned with the adjacent end of the guide tube 34, as shown in full line. This affords ample idling play or tolerance motion of the yoke 38 not only for minor vibrations of the drum 15 as transmitted to the yoke, but also for up to maximum backlash or retraction as shown in dash outline, as the rotating drum 15 attains an amplitude of vibration calling for balancing.

When an unbalanced condition in the drum 15 generates: a vibration of an amplitude desirably requiring correc-- tion, such vibration, as amplified through the lever 29' and transmitted by the wire 33, causes the yoke 38 to reach its maximum extended or protracted position, as shown in dot-dash outline in FIGURE 3. This releases.

the crank pin 39 from restraint so that the distributor valve shaft 40 can rotate with the manifold housing member 47 by virtue of slip clutch means as afforded by an elastomeric O-ring 55 carried in a peripheral groove 57 in the bearing stud 43 and affording frictional coupling engagement with the surfaces defining the groove and with the opposing surface defining the bearing wall of the bore 44. Clutched corotation of the distributor valve disk 41 with the distributor housing member 47 and partition 45 is thus substantially synchronized or co-ordinated with exposure of the one or pair of the distributor orifices 50 communicating with the one or pair of the balancing pocket compartments 54 generally opposite the unbalancing Weight or mass in the drum as identified schematically at M in FIGURES 8 and 9.

Means are provided synchronized or co-ordinated in operation with the proportional control valve 41 for supplying or charging the water inlet manifold chamber 48 with balancing liquid. Herein this is conveniently effected on a demand basis controlled by the yoke 38. To this end, as the yoke 38 is cranked by the crank pin 39 as released during a vibrating cycle of the unbalanced rotor 15, the yoke functions to engage a trip projection 58 (FIGS. 2 and 3) extending into its path from a valve such as a reciprocable spool valve 59 normally urged by means such as a biasing compression spring 60 into idling position and mounted in a valve body 61 suitably carried by the mounting frame 37.

In its idling position, the spool valve 59 closes off an air pressure duct 62 (FIG. 2) which leads from an air pressure source such as a compressor 63 (FIG. 1) operated by the power means 27. When the yoke 38 trips the valve 59 in opposition to its biasing spring 60, communication is established between the air pressure supply duct 62 and a pressure delivery duct 64 leading to an air pressure responsive diaphragm valve actuator 65 (FIGS. 1 and 7) which then drives a normally closed reciprocable shut off valve 67 to open communication of a liquid source conduit 68 with the manifold supply conduit 49. During operation of the machine, a constant liquid pressure head is maintained in the supply conduit 68 by a suitable pump 69 connected as by a suction conduit 70 to the lower or sump area within the tank 13.

Since the balancing water supply is under constant head of pressure in the supply conduit 68, immediately upon opening of the shut off valve 67, balancing water flows into the manifold chamber 48 and is distributed to the exposed orifice or orifices 50, whence it passes by water pressure and centrifugal force through the connecting supply duct or ducts 53 to the appropriate balancing pocket or pockets 54 to counterbalance the load eccentricity and substantially balance the drum 15. The valve 59 is a slow-to-close type valve that will remain open continuously as long as it is actuated by yoke 38 at each revolution; therefore as long as there is suflicient off balance to allow the revolution of proportional control valve 41, balance water will flow into manifold chamber 48.

A typical counterbalancing operation is schematically depicted in FIGURE 8 wherein it is assumed that the eccentric mass M is directly opposite one of the balancing pockets 54. As the eccentric force represented by the straight solid directional arrow imposes maximum vibrational deflection toward the left as viewed on the pylon 19, and the yoke 38 is actuated to release the distributor valve 41 to rotate, as shown by the curved directional arrow, in phase with the load M, the orifice communicating with the balancing pocket 54 opposite the load is open while the remaining orifices are closed by the distributor valve. The trigger arm 38 will be positioned or provide the correct phase of valve 41 with respect to the off balance load before the crank pin 39 passes over the top dead center. Then, in the continuing rotation of the distributor valve 41 in phase with the load M, the balancing water will continuously flow into the manifold as triggered by the yoke 38 and fully transfer into the appropriate balancing pocket or pockets during the entire revolution. If the unbalanced condition persists within the range of amplitude requiring correction, the balancing process will continue until an adequately balanced condition is effected.

By virtue of the self-orienting relationship of the distributor valve disk 41 and the distributor ports 50, any incremental relative circumferential load imbalance of the drum 15 can be adequately counterbalanced.

As the air control valve 59 returns to normal position after the triggering yoke 38 rotates beyond the trip projection 58, communication is effected between the air conduit 64 and a bleed-off conduit 71. This leads from the valve body 61 to suitable leakage or bleed-off timing or suction means to regulate and effect timed action of the shut-off valve control 65 for properly co-ordinating operation of valve 67 throughout the balancing cycle of the system.

Instead of a yoke and crank pin arrangement for coupling the vibration transmitting element with the distributor disk valve shaft, an alternative embodiment or modification as depicted in FIGURES 4 and 5 may be utilized. In this form, the distributor disk valve shaft 40' has on its rear end a rigid eccentric projection 71 which is engaged by a stop finger means 72 normally located in the path of the projection and thereby restraining the valve against rotation with the drum shaft. The projection 71 presents a face to the stop finger 72 on which the finger is longitudinally reciprocably slidable in response to amplified drum vibrations transmitted to the finger by the flexible transmission element 33'. When the amplitude of transmitted vibration reaches the point of desirability of correction, the free end of the finger 72 clears the projection 71, permitting the shaft 40' to couple for co-rotation with the drum shaft for at least a full rotation, to the same effect as the yoke and pin controlled shaft 40 to effect counterbalancing distribution of liquid to the appropriate counterbalancing pocket or pockets 54 of the drum. As the shaft 40' rotates in a balancing cycle, the project-ion 71 serves as a trigger, similarly as the yoke 38, to trip the valve trip projection 58 for providing a flow of balancing water into the manifold of the balancing system.

Although minor modifications might be suggested by those versed in the art, it should be understood that I wish to embody within the scope of the patent warranted hereon all such modifications as reasonably and properly come within the scope of my contribution to the art.

The embodiments of the invention in which an exclusive property or privilege is claimed are defined as follows:

1. A laundry apparatus including a rotatably driven receptacle and means providing generally peripherally located counter-balancing liquid receiving pockets on said receptacle,

a supporting pylon mounting the receptacle on a generally horizontal axis,

means for supplying counterbalancing liquid to selected ones of said liquid receiving pockets located at the periphery of said receptacle,

means for selective distribution of balancing liquid to said pockets comprising a distributor assembly including a control valve, and means for controlling the control valve including a vibration magnifying linkage and lever coupling,

an off-balance motion indicator lever arm projecting from said pylon and connecting the coupling to the Py and transmission means connected to said magnifying coupling and to said control valve.

2. Means for controlling distribution of balancing liquid to a rotatable laundry receptacle member and the like which comprises:

means defining a liquid manifold including a surface rotatable with said member and having a plurality of balancing liquid distribution orifices at spaced intervals,

a control valve mounted to rotate with said surface and also to remain relatively stationary,

said valve having orifice selecting means adapted to close the orifices selectively whereby to effect selection of the orifices through which balancing liquid is to be distributed,

means for sensing eccentric forces in the rotation of said member and including a connection with said valve normally restraining the valve against rotation with said surface but operative in response to eccentric forces of a magnitude desirably to be corrected to release the valve for corotation with the surface and with said valve means automatically oriented for proper distribution of balancing liquid,

and means for charging the manifold with balancing liquid including a normally closed shut off valve and means responsively related to said sensing means to be actuated for opening said shut olf valve to charge the manifold in coordinated relation to release of said valve.

3. Centrifuging apparatus comprising, in combination, a rotary receptacle adapted to receive materials to be centrifuged and including a plurality of peripheral balance pockets,

means providing a stationary base support,

means mounting said receptacle for rotational and limited eccentric vibratory movements relative to said base support,

drive means for rotating said receptacle,

fluid manifold means including a member rotatably coupled with, and on the axis of rotation of, said receptacle,

a plurality of distribution conduits individually and respectively interconnecting each of said pockets with said fluid manifold means,

means providing a liquid supply passage connected to said manifold means to supply liquid under pressure to said pockets through said distribution conduits,

a valve member for controlling distribution of liquid from the manifold to said conduits including slip clutch means for corotationally driving the valve member with said manifold member,

restraining means connected to said valve member and normally restraining it against rotation with said manifold member,

normally closed valve means in said supply passage,

control means for said valve means,

and means sensitive to vibratory movements of said mounting means and interconnected with said restraining means for actuating the restraining means to release said valve member to rotate with said manifold member in phase with a receptacle load responsible for such vibrations so as to effect liquid flow to the pockets selectively to counterbalance the receptacle and at least reduce the vibrations thereof,

said restraining means when released actuating said control means for opening said valve means to effect charging of the manifold with balancing liquid to be distributed under the control of said valve member.

4. In a laundry machine, means for controlling distribution of balancing liquid to balancing pockets of a rotatably driven clothes receptacle subject to load eccentricities which cause vibrations in a supporting mount for said receptacle,

a manifold having liquid distribution means therein for controlling distribution of liquid from the manifold to said pockets,

means for supplying liquid under pressure to said manifold and including a normally closed shut oif valve,

and means for co-ordinating operation of said distributor means and opening of said normally closed valve comprising:

an off-balance motion indicator arm rigid with and projecting from said mount,

a motion amplifying oscillatable lever,

a link connecting the lever to said indicator arm for oscillation of the lever responsive to vibratory movements of the mount,

and a transmission element connected to the le- Ver for transmitting amplified vibratory movements to control operations of said distributor and to open said valve.

5. A device for controlling distribution of balancing liquid to respective pockets provided on a rotary member mounted on a shaft carried by a pylon structure subject to vibrations when the rotary member rotates with an eccentric load therein,

a manifold including a member rotatable with the rotary member and having a plurality of orifices respectively leading to said pockets,

a distributor valve in said manifold and carried on a rotary shaft having an end outside of said manifold,

a combination restraining and trip structure mounted eccentrically on said shaft end,

means normally holding said eccentric structure to restrain said shaft and thereby the distributor valve from rotating with said manifold member but responsive to vibrations of said pylon to release said eccentric structure and thus the restraint upon rotation of the shaft and distributor valve,

and means for charging the manifold continuously with liquid under pressure on demand for balancing liquid including a trip device mounted normally out of engagement with said eccentric structure but engageable thereby when the eccentric structure is released.

6. A device as defined in claim 5, wherein said eccentric structure comprises a crank pin on the shaft and a yoke engaged therewith.

7. A device as defined in claim 5, wherein said restraining structure comprises an eccentric projection and said vibration responsive means comprises a finger normally engaging said eccentric projection but releasable therefrom when the amplitude of vibration of the pylon reaches a predetermined value.

8. A centrifuge construction including a base structure having a pylon structure mounted thereon,

a centrifuge rotor having a shaft rotatably supported by the pylon and transmitting eccentric load forces to vibrate the pylon,

means for driving the shaft rotatably,

a Water tank about the centrifuge rotor having a sump portion,

said rotor having a plurality of circumferentially spaced balancing pocket receptacles,

a manifold at least in part rotatable concentrically with said shaft and having respective conduits leading therefrom to said balancing pocket receptacles,

distributor valve means in said manifold,

a supply passage structure leading from said sump to said manifold and including a pump,

a valve normally closing the supply passage,

compressed air actuated means for operating said normally closed valve to open the same,

a compressor operated by said driving means and connected with said air actuated means,

a control valve normally disconnecting the air pressure from said air actuated means and including a trip device adjacent to said manifold,

and mechanical control means connected to said pylon and including means to control said distributor valve and to trip said trip means in co-ordinated relation when the pylon vibrates with predetermined amplitude.

9. centrifuging apparatus comprising, in combination,

a rotary receptacle adapted to receive materials to be centrifuged and including a plurality of peripheral balance pockets,

means providing a stationary base support,

means mounting said receptacle for rotational and limited eccentric vibratory movements relative to said base support,

drive means for rotating said receptacle,

fluid manifold means including a member rotatably coupled with, and on the axis of rotation of, said receptacle,

a plurality of distribution conduits individually and respectively interconnecting each of said pockets with said fluid manifold means,

means providing a liquid supply passage connected to said manifold means to supply liquid under pressure to said pockets through said distribution conduits,

a valve member for controlling distribution of liquid from the manifold to said conduits including slip clutch means for corotationally driving the valve member with said manifold member,

restraining means connected to said valve member and normally restraining it against rotation with said manifold member,

and means sensitive to vibratory movements of said mounting means and interconnected with said restraining means for actuating the restraining means to release said valve member to rotate with said manifold member in phase with a receptacle load responsible for such vibrations so as to effect liquid flow to the pockets selectively to counterbalance the receptacle and at least reduce the vibrations thereof.

References Cited by the Examiner UNITED STATES PATENTS 2,461,643 2/1949 Hemmeter 210-144 X 2,498,420 2/ 1950 Hemmeter 210-144 X 2,534,268 12/1950 Kahn et al. 210144 X 2,534,269 12/1950 Kahn et al. 210-144 X 2,538,246 1/1951 Holm-Hansen 210144 2,647,386 8/1953 Keiper 68--24 2,895,023 7/1959 Blum 210144 X 3,135,688 6/1964 Compans et al. 210-144 3,142,641 7/1964 Lachat 68-24 X FOREIGN PATENTS 136,390 7/ 1952 Sweden.

REUBEN FRIEDMAN, Primary Examiner. D. M. RIESS, Assistant Examiner. 

1. A LAUNDRY APPARATUS INCLUDING A ROTATABLY DRIVEN RECEPTACLE AND MEANS PROVIDING GENERALLY PERIPHERALLY LOCATED COUNTER-BALANCING LIQUID RECEIVING POCKETS ON SAID RECEPTACLE, A SUPPORTING PYLON MOUNTING THE RECEPTACLE ON A GENERALLY HORIZONTAL AXIS, MEANS FOR SUPPLYING COUNTERBALANCING LIQUID TO SELECTED ONES OF SAID LIQUID RECEIVING POCKETS LOCATED AT THE PERIPHERY OF SAID RECEPTACLE, MEANS FOR SELECTIVE DISTRIBUTION OF BALANCING LIQUID TO SAID POCKETS COMPRISING A DISTRIBUTOR ASSEMBLY INCLUDING A CONTROL VALVE, 